EP2677126B1 - Valve opening/closing timing control device - Google Patents
Valve opening/closing timing control device Download PDFInfo
- Publication number
- EP2677126B1 EP2677126B1 EP12747141.5A EP12747141A EP2677126B1 EP 2677126 B1 EP2677126 B1 EP 2677126B1 EP 12747141 A EP12747141 A EP 12747141A EP 2677126 B1 EP2677126 B1 EP 2677126B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- rotary element
- driven rotary
- fitting
- partitions
- control device
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Not-in-force
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/02—Valve drive
- F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
- F01L1/047—Camshafts
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/356—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear making the angular relationship oscillate, e.g. non-homokinetic drive
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/02—Valve drive
- F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
- F01L1/047—Camshafts
- F01L2001/0476—Camshaft bearings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L2303/00—Manufacturing of components used in valve arrangements
Definitions
- the present invention relates to a valve timing control device including a driving rotary element synchronously rotatable with a crankshaft; a driven rotary element mounted coaxially with the driving rotary element and synchronously rotatable with a camshaft; and a plurality of partitions provided in the driven rotary element each for dividing a fluid pressure chamber formed between the driving rotary element and the driven rotary element into a regarded angle chamber and an advanced angle chamber.
- the fastening pressure applied to the driven rotary element is increased because of a small contacting area between the camshaft and the driven rotary element.
- an aluminum material of low rigidity is often used for manufacturing the driven rotary element, and thus the driven rotary element is easily deformed.
- a connecting element is disposed between the driven rotary element and the camshaft. This increases the contacting area between the camshaft and the driven rotary element to reduce a pressing force exerted upon the driven rotary element per unit area, as a result of which the deformation of the driven rotary element can be prevented.
- Japanese Unexamined Patent Application Publication No. 2006-183590 discloses a technique for forming a recess for receiving the connecting element press-fittingly in the driven rotary element and also forming a recess for receiving a bushing press-fittingly in the back side of the driven rotary element (see PTL 1). This balances the degrees of deformation in diameter in both the surfaces of the element and prevents the driven rotary element from deforming outward of the surface.
- a valve opening/closing timing control device according to the preamble of claim 1 of the present invention is known from US 2010/0199937 A1 .
- valve timing control device comprising a driving rotary element synchronously rotatable with a crankshaft; a driven rotary element mounted coaxially with the driving rotary element and synchronously rotatable with a camshaft; a plurality of second partitions provided in the driven rotary element each for dividing a fluid pressure chamber formed between the driving rotary element and the driven rotary element into a regarded retarded angle chamber and an advanced angle chamber; and a connecting element having a press fitting portion that is press-fitted into a recess formed in the driven rotary element for connecting the driven rotary element to the camshaft.
- the object of the present invention is to provide a valve timing control device enabling simplification of the manufacturing process and reduction of the number of parts while suppressing deformation of the driven rotary element.
- a first characteristic feature of the valve timing control device lies in comprising a driving rotary element synchronously rotatable with a crankshaft; a driven rotary element mounted coaxially with the driving rotary element and synchronously rotatable with a camshaft; a plurality of partitions provided in the driven rotary element each for dividing a fluid pressure chamber formed between the driving rotary element and the driven rotary element into a regarded angle chamber and an advanced angle chamber; and a connecting element having a press fitting portion that is press-fitted into a recess formed in the driven rotary element for connecting the driven rotary element to the camshaft, wherein the press fitting portion includes a plurality of fitting segments spaced apart from each other along a rotational direction to fit to an inner circumference of the recess, and at least one of centerlines of the fitting segments extending in a radial direction does not overlap any of the partitions.
- the driven rotary element includes a cylindrical portion formed adjacent a rotational center thereof and a plurality of partitions circumferentially provided at intervals in an outer circumference of the cylindrical portion.
- the present invention provides a technique for minimizing the influence of the deformation of the driven rotary element caused by the pressing of the connecting element. Providing any one of the fitting segments radially overlaps any one of the partitions, a contact portion of the driven rotary element coming into contact with the fitting segment is deformed radially outward. With such deformation, the partition associated with the contact portion is also enlarged in diameter.
- the driven rotary element is deformed only at the side adjacent to the recess, and thus the partition moves to the opposite side to the recess and deforms. As the partition has a predetermined radial dimension, the deformation of the partition at an end thereof becomes great.
- At least one of the plurality of fitting segments formed in the connecting element is arranged so as not to radially overlap the corresponding partition of the driven rotary element.
- a second characteristic feature of the valve timing control device of the present invention lies in that all of the radially extending centerlines of the fitting segments are configured not to overlap any of the partitions.
- any of the partitions is not influenced by or is influenced a little by the deformation of the driven rotary element caused by the pressing of the fitting segments. More particularly, the deformation of the driven rotary element caused by the pressing of the fitting segments becomes a maximum on the centerlines of the fitting segments extending in the radial direction.
- the deformation of the driven rotary element as a whole can be a minimum by arranging the centerlines of the fitting segments so as not to overlap the partitions.
- a third characteristic feature of the valve timing control device of the present invention lies in that all of the fitting segments are configured not to radially overlap any of the partitions other than the partition that is provided with at least one of a contact portion coming into contact with the driving rotary element for limiting relative movement between the driving rotary element and the driven rotary element and a lock mechanism for locking the driving rotary element and the driven rotary element in a predetermined rotational phase.
- At least one of the partitions of the driven rotary element is provided with the lock mechanism for locking the driving rotary element and the driven rotary element in the predetermined relative phase, or the contact portion coming into contact with the driving rotary element when the driven rotary element is rotated to the most advanced angle side or the most regarded angle side to limit further relative movement therebetween.
- the lock mechanism When the lock mechanism is provided, the partition having the lock mechanism becomes larger than the remaining partitions in circumferential dimension because a lock pin should be provided.
- the contact portion is provided, the partition having the contact portion becomes larger than the remaining partitions in circumferential dimension because the contact portion should stand a shock of contact.
- the rigidity of the partition having the lock mechanism or the contact portion becomes greater than that of the remaining partitions.
- the partition that is provided with the lock mechanism or the like and having high rigidity is referred to as a high-rigidity partition, while the remaining partitions having low rigidity are referred to as low-rigidity partitions hereinafter.
- none of the fitting segments agree with the low-rigidity partitions. If any of the fitting segments agrees with the high-rigidity partition or low-rigidity partition in the radial direction, the outward surface deformation caused by the radial agreement between the fitting segment and the low-rigidity partition is greater than the outward surface deformation caused by the radial agreement between the fitting segment and the high-rigidity partition. Thus, the outward surface deformation can be minimized by the arrangement in which none of the fitting segments corresponds to the low-rigidity partition.
- a fourth characteristic feature of the present invention lies in that at least one of the plurality of fitting segments is configured to radially overlap the partition that is provided with at least one of the contact portion and the lock mechanism in the radial direction.
- the fitting segment agrees with the high-rigidity partition if it is unavoidable that any of the fitting segments radially agrees with any of the partitions.
- the outward surface deformation can be minimized even if somewhat deformation inevitably occurs, thereby to suppress overall deformation of the driven rotary element as much as possible.
- a fifth characteristic feature of the present invention lies in that the connecting element has an axial support portion that supports in a through bore formed in the driving rotary element.
- the connecting element is allowed to have a function to axially support the driving rotary element.
- the connecting element axially supports the driving rotary element to reliably maintain the driving rotary element coaxially with the driven rotary element, while the construction can be simplified. As a result, the posture of the driven rotary element is stabilized.
- a sixth characteristic feature of the present invention lies in providing a guide mechanism for guiding and positioning the driven rotary element and the connecting element in the predetermined rotational phase.
- the driven rotary element and the connecting element can be guided and positioned in the predetermined rotational phase through the guide mechanism, which facilitates the positioning of the driven rotary element and the connecting element.
- a valve timing control device according to an embodiment of the present invention that is applied to an automobile engine will be described hereinafter in reference to Figs. 1 and 5 .
- the valve timing control device is provided with a steel housing 1 (an example of a driving rotary element) that is synchronously rotatable with a crankshaft C of an engine, and an aluminum inner rotor 3 (an example of a driven rotary element) that is synchronously rotatable with a camshaft 2 of the engine.
- the housing 1 and the inner rotor 3 are coaxially arranged on an axis X.
- the housing 1 includes a front plate 4 mounted on a front side thereof opposite to the camshaft 2, a sprocket 5 mounted on a rear side thereof adjacent to the camshaft 2, and an outer rotor 6 mounted between the front plate 4 and the sprocket 5.
- the front plate 4, sprocket 5 and outer rotor 6 are fixedly screwed.
- the housing 1 may be integrally formed as a unit instead of fixedly screwing the front plate 4, sprocket 5 and outer rotor 6 together.
- a rear plate may be mounted instead of the sprocket 5, and the sprocket may be provided at an outer circumference of the outer rotor 6.
- a rotational driving force is transmitted to the sprocket 5 through a power transmission mechanism (not shown) to rotate the outer rotor 6 in a rotational direction S (see Fig. 2 ).
- the inner rotor 3 is rotated in the rotational direction S to rotate the camshaft 2.
- a cam (not shown) provided in the camshaft 2 pushes down on an intake valve (not shown) of the engine.
- a plurality of first partitions 8 project inward in a radial direction from an inner circumference of the outer rotor 6.
- the first partitions 8 are spaced apart from each other along the rotational direction S.
- a plurality of second partitions 9 project outward in the radial direction from an outer circumference of the inner rotor 3.
- the second partitions 9 are also spaced apart from each other along the rotational direction S in the same manner as the first partitions 8.
- the first partitions 8 are configured to divide space between the outer rotor 6 and the inner rotor 3 into a plurality of fluid pressure chambers.
- the second partitions 9 are configured to divide each of the fluid pressure chambers into an advanced angle chamber 11 and a retarded angle chamber 12.
- sealing elements SE are provided in positions of the first partitions 8 opposed to the outer circumference of the inner rotor 3 and in positions of the second partitions 9 opposed to the inner circumference of the outer rotor 6, respectively.
- a connecting element 22 and the camshaft 2 are formed an advanced angle passage 13 for connecting each advanced angle chamber 11 to a feed/discharge mechanism KK for allowing and intercepting feed or discharge of engine oil, a retarded angle passage 14 for connecting each regarded angle chamber 12 to the feed/discharge mechanism KK, and a lock passage 15 for connecting the feed/discharge mechanism KK to a lock mechanism RK for locking the inner rotor 3 and outer rotor 6 in a predetermined relative rotational phase.
- the feed/discharge mechanism KK includes an oil pan, an oil motor, a fluid control valve OCV for allowing and intercepting feed or discharge of engine oil to/from the advanced angle passage 13 and the retarded angle passage 14, a fluid switch valve OSV for allowing and intercepting feed or discharge of engine oil to/from the lock passage 15, and an electric control unit ECU for controlling operation of the fluid control valve OCV and fluid switch valve OSV.
- the feed/discharge mechanism KK is controlled, the relative rotational phase of the inner rotor 3 and outer rotor 6 is displaced in an advanced angle direction (arrow S1 in Fig. 2 ) or a regarded angle direction (arrow S2 in Fig. 2 ) or is maintained in a desired phase.
- the inner rotor 3, connecting element 22 and camshaft 2 are fastened through a bolt 21.
- the bolt 21 is fastened to a female screw 2b formed in the back of a receiving bore 2c formed in an extreme end of the camshaft 2.
- the inner rotor 3 is integrally assembled to the extreme end of the camshaft 2 through the connecting element 22.
- a first hollow 23 for accommodating the head of the bolt 21 is formed in a front surface of the inner rotor 3, while a second hollow 24 (an example of a recess) is formed in a rear surface of the inner rotor 3 for receiving press-fittingly a front part 26 (an example of a press-fitting portion) of the connecting element 22.
- a through bore 25 is formed between the first hollow 23 and the second hollow 24 for receiving the bolt 21.
- a plurality of cutaway segments 27 are spaced apart from each other along the rotational direction S in the front part 26 of the connecting element 22.
- Each section defined between the adjacent cutaway segments 27 acts as a fitting segment 28 that is press-fitted into an inner circumference of the second hollow 24.
- a plurality of the fitting segments 28 are arranged along a circumferential direction of the connecting element 22 at intervals of 90 degrees, for example.
- a width of each fitting segment 28 in an axial direction is substantially the same as or greater than a depth of the second hollow 24.
- a rear part 29 (an example of an axial support portion) of the connecting element 22 is supported in a round bore 30 of the sprocket 5. This enables the connecting element 22 to have a function to axially support the housing 1.
- the inner rotor 3 and the housing 1 are securely maintained in a coaxial relationship while the construction can be simplified, which stabilizes the posture of the inner rotor 3.
- the connecting element 22 has an opening 31 formed in a front surface thereof for receiving the bolt 21, and a recess 32 formed in a rear surface thereof for receiving the extreme end of the camshaft 2.
- a front pin-receiving hole 3a is formed in the inner rotor 3
- a rear pin-receiving hole 2a is formed in the extreme end of the camshaft 2
- an intermediate pin-receiving hole 22a is formed in the connecting element 22, respectively.
- a gap between the through bore 25 of the inner rotor 3 and the bolt 21, a gap between the opening 31 of the connecting element 22 and the bolt 21, and a gap between the receiving bore 2c of the camshaft 2 and the bolt 21 act together as the advanced angle passage 13.
- a pin P is inserted into the pin-receiving hole 3a of the inner rotor 3 and the pin-receiving hole 22a of the connecting element 22 to press fit the front part 26 of the connecting element 22 to the second hollow 24 of the inner rotor 3. Then, the pin P advances into the pin-receiving hole 2a formed in the extreme end of the camshaft 2 to insert the extreme end of the camshaft 2 to the recess 32 of the connecting element 22. As a result, the inner rotor 3, the connecting element 22 and the extreme end of the camshaft 2 are positioned in the predetermined relative rotational phase, thereby to form the advanced angle passage 13, the retarded angle passage 14 and the lock passage 15.
- the pin P and pin-receiving holes 3a and 22a act as a guide mechanism together for allowing the inner rotor 3 and the connecting element 22 to be positioned in the predetermined relative rotational phase.
- the inner rotor 3 and the connecting element 22 are guided and positioned in the predetermined rotational phase through the guide mechanism (pin P and pin-receiving holes 3a and 22a). This facilitates the positioning of the inner rotor 3 and the connecting element 22.
- none of the fitting segments 28 may overlap any of the second partitions 9, for example.
- the connecting element 22 is press-fitted into the second hollow 24, the portions of the inner rotor 3 corresponding to the fitting segments are somewhat deformed to be radially enlarged, but are not associated with any of the second partitions 9.
- none of the second partitions 9 are deformed in corners.
- fitted segments 41 in the inner rotor 3 are all deformed to the same extent, which can prevent eccentricity of the inner rotor 3.
- Fig. 4 shows the configuration in which none of the fitting segments 28 overlap the second partitions 9, it is sufficient that at least one of the fitting segments 28 does not overlap the corresponding second partition 9. This is because the deformation of the inner rotor 3 can be a minimum since the portion where the fitting segment 28 does not overlap the corresponding second partition 9 has no influence on the change of the posture of the second partition 9.
- the second partitions 9 may be arranged so as not to overlap centerlines CL of the respective fitting segments 28 extending in the radial direction.
- the deformation of the inner rotor 3 caused by the pressing of the fitting segments 28 becomes a maximum on the centerlines CL of the fitting segments 28 extending in the radial direction.
- the outward surface deformation of the whole inner rotor 3 can be minimized by arranging the second partitions 9 so as not to overlap the centerlines of the fitting segments 28.
- any of the second partitions 9 is not influenced by or is influenced a little by the deformation of the inner rotor 3 caused by the pressing of the fitting segments 28.
- part of the fitting segments 28 overlaps the second partition 9 that is provided with the lock mechanism RK of the plurality of second partitions 9 in the radial direction, and the remaining fitting segments 28 do not overlap the second partitions 9 that are not provided with the lock mechanism RK.
- the second partition 9 that is provided with the lock mechanism RK is greater than the remaining second partitions in circumferential dimension and rigidity because the lock pin should be provided.
- the second partition that is provided with the lock mechanism RK is referred to as a high-rigidity partition 9a, while the remaining second partitions are referred to as low-rigidity partitions 9b hereinafter.
- the high-rigidity partition 9a is selected as the second partition 9 to overlap. More particularly, the high-rigidity partition 9a is not much subject to the influence of the pressing of the connecting element 22 because of its high rigidity. Therefore, the outward surface deformation in the corresponding fitted segment 41 is diminished, which results in the minimal overall deformation of the inner rotor 3.
- the fitted segments 41 fitted to the remaining three fitting segments 28 are formed in cylindrical portions of the inner rotor 3. Thus, while the cylindrical portions are deformed by the pressing of the fitting segments 28, such deformation has no influence on any of the low-rigidity partitions 9b.
- only one fitting segment 28 radially overlaps the high-rigidity partition 9a that is provided with the lock mechanism RK.
- a plurality of the fitting segments 28 may overlap one high-rigidity partition 9a.
- a plurality of the high-rigidity partitions 9a may correspond to the plurality of fitting segments 28, respectively. In any case, the above-described effect of suppressing the deformation of the inner rotor 3 can be achieved.
- Each fitting segment 28 of the connecting element 22 may be shaped as shown in Figs. 7 and 8 . More particularly, the fitting segment 28 may be formed in a region extending from the front side to the back side of the connecting element 22 as shown in Fig. 7 .
- the connecting element 22 may have a combination of cutaway parts 27 each having a flat surface and fitting segments 28 each having a cylindrical surface.
- the fitting segments 28 may be formed by chamfering four corners of a square material.
- the cutaway parts 27 may be formed by cutting four sections away from a disk material to flat surfaces.
- any of the above-described arrangements can provide the connecting element 22 that can minimize the deformation of the inner rotor 3.
- the connecting element 22 shown in Fig. 8 in particular, is easy to process in shape, and thus can be manufactured cost-effectively.
- the present invention is applicable to a valve timing control device for an internal combustion engine of an automobile, for example.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
Description
- The present invention relates to a valve timing control device including a driving rotary element synchronously rotatable with a crankshaft; a driven rotary element mounted coaxially with the driving rotary element and synchronously rotatable with a camshaft; and a plurality of partitions provided in the driven rotary element each for dividing a fluid pressure chamber formed between the driving rotary element and the driven rotary element into a regarded angle chamber and an advanced angle chamber.
- When the driven rotary element is bolted to the camshaft, the fastening pressure applied to the driven rotary element is increased because of a small contacting area between the camshaft and the driven rotary element. In general, an aluminum material of low rigidity is often used for manufacturing the driven rotary element, and thus the driven rotary element is easily deformed.Under the circumstances, a connecting element is disposed between the driven rotary element and the camshaft. This increases the contacting area between the camshaft and the driven rotary element to reduce a pressing force exerted upon the driven rotary element per unit area, as a result of which the deformation of the driven rotary element can be prevented.
- Various parts are manufactured in various component facilities and delivered to an assembly shop to assemble the driven rotary element to the camshaft. The driven rotary element, the driving rotary element and the connecting element of all the components are manufactured in the same component facility and delivered as an assembled unit. The connecting element is press-fitted to a recess formed in one side of the driven rotary element and delivered as an integrated unit. Such an integrated configuration advantageously alleviates the trouble in delivery and facilitates the assembling work of the camshaft.
- On the other hand, when the connecting element is press-fitted to the recess of the driven rotary element, only the surface of the driven rotary element provided with the recess is enlarged in diameter, as a result of which the entire driven rotary element may disadvantageously be deformed outward of the surface in a direction opposite to the recess. As a measure for overcoming such a disadvantage, Japanese Unexamined Patent Application Publication No.
2006-183590 - A valve opening/closing timing control device according to the preamble of
claim 1 of the present invention is known fromUS 2010/0199937 A1 . - At this point, reference shall additionally be made to the prior
art document PTL 2 which discloses a valve timing control device comprising a driving rotary element synchronously rotatable with a crankshaft; a driven rotary element mounted coaxially with the driving rotary element and synchronously rotatable with a camshaft; a plurality of second partitions provided in the driven rotary element each for dividing a fluid pressure chamber formed between the driving rotary element and the driven rotary element into a regarded retarded angle chamber and an advanced angle chamber; and a connecting element having a press fitting portion that is press-fitted into a recess formed in the driven rotary element for connecting the driven rotary element to the camshaft. -
- PTL 1: Japanese Unexamined Patent Application Publication No.
2006-183590 - PTL 2:
WO 2010/12 89 76 A1 - However, in the technique disclosed in
PTL 1 orPTL 2, the degrees of deformation in diameter in both the surfaces of the driven rotary element are not necessarily canceled with each other due to, for example, a dimensional error in the bushing, connecting element, or recesses. As a result, the outward surface deformation may still be observed in the driven rotary element. This technique requires a step for press fitting the bushing in addition to the step for press fitting the connecting element. Therefore, not only the number of components is increased to lead to troublesome working, but also the outward surface deformation of the driven rotary element cannot be reliably prevented. Hence, the conventional technique noted above cannot be regarded as a rational art for providing the valve timing control device. - The object of the present invention is to provide a valve timing control device enabling simplification of the manufacturing process and reduction of the number of parts while suppressing deformation of the driven rotary element.
- This object is solved by a valve timing control device having the features according to the
patent claim 1. A first characteristic feature of the valve timing control device according to the present invention lies in comprising a driving rotary element synchronously rotatable with a crankshaft; a driven rotary element mounted coaxially with the driving rotary element and synchronously rotatable with a camshaft; a plurality of partitions provided in the driven rotary element each for dividing a fluid pressure chamber formed between the driving rotary element and the driven rotary element into a regarded angle chamber and an advanced angle chamber; and a connecting element having a press fitting portion that is press-fitted into a recess formed in the driven rotary element for connecting the driven rotary element to the camshaft, wherein the press fitting portion includes a plurality of fitting segments spaced apart from each other along a rotational direction to fit to an inner circumference of the recess, and at least one of centerlines of the fitting segments extending in a radial direction does not overlap any of the partitions. - In general, the driven rotary element includes a cylindrical portion formed adjacent a rotational center thereof and a plurality of partitions circumferentially provided at intervals in an outer circumference of the cylindrical portion. When the connecting element is press-fitted to such a driven rotary element in connecting the camshaft, the driven rotary element is inevitably deformed more or less as described above.
- The present invention provides a technique for minimizing the influence of the deformation of the driven rotary element caused by the pressing of the connecting element. Providing any one of the fitting segments radially overlaps any one of the partitions, a contact portion of the driven rotary element coming into contact with the fitting segment is deformed radially outward. With such deformation, the partition associated with the contact portion is also enlarged in diameter. Here, the driven rotary element is deformed only at the side adjacent to the recess, and thus the partition moves to the opposite side to the recess and deforms. As the partition has a predetermined radial dimension, the deformation of the partition at an end thereof becomes great.
- In order to eliminate such a disadvantage, according to the first characteristic feature of the present invention, at least one of the plurality of fitting segments formed in the connecting element is arranged so as not to radially overlap the corresponding partition of the driven rotary element. With such an arrangement, even if the cylindrical portion of the driven rotary element is deformed and enlarged in diameter, no partition is present radially outward of the deformed portion, and thus no outward deformation of the partition occurs. In this manner, it is possible to minimize the outward surface deformation of the driven rotary element by diminishing the number of the partitions radially corresponding to the fitting segment.
- A second characteristic feature of the valve timing control device of the present invention lies in that all of the radially extending centerlines of the fitting segments are configured not to overlap any of the partitions.
- With the above-noted arrangement in which all of the radially extending centerlines of the fitting segments are configured not to overlap any of the partitions, any of the partitions is not influenced by or is influenced a little by the deformation of the driven rotary element caused by the pressing of the fitting segments. More particularly, the deformation of the driven rotary element caused by the pressing of the fitting segments becomes a maximum on the centerlines of the fitting segments extending in the radial direction. Thus, the deformation of the driven rotary element as a whole can be a minimum by arranging the centerlines of the fitting segments so as not to overlap the partitions.
- A third characteristic feature of the valve timing control device of the present invention lies in that all of the fitting segments are configured not to radially overlap any of the partitions other than the partition that is provided with at least one of a contact portion coming into contact with the driving rotary element for limiting relative movement between the driving rotary element and the driven rotary element and a lock mechanism for locking the driving rotary element and the driven rotary element in a predetermined rotational phase.
- In general, at least one of the partitions of the driven rotary element is provided with the lock mechanism for locking the driving rotary element and the driven rotary element in the predetermined relative phase, or the contact portion coming into contact with the driving rotary element when the driven rotary element is rotated to the most advanced angle side or the most regarded angle side to limit further relative movement therebetween. When the lock mechanism is provided, the partition having the lock mechanism becomes larger than the remaining partitions in circumferential dimension because a lock pin should be provided. Similarly, when the contact portion is provided, the partition having the contact portion becomes larger than the remaining partitions in circumferential dimension because the contact portion should stand a shock of contact. As a result, the rigidity of the partition having the lock mechanism or the contact portion becomes greater than that of the remaining partitions. The partition that is provided with the lock mechanism or the like and having high rigidity is referred to as a high-rigidity partition, while the remaining partitions having low rigidity are referred to as low-rigidity partitions hereinafter.
- In the arrangement having the third characteristic feature, none of the fitting segments agree with the low-rigidity partitions. If any of the fitting segments agrees with the high-rigidity partition or low-rigidity partition in the radial direction, the outward surface deformation caused by the radial agreement between the fitting segment and the low-rigidity partition is greater than the outward surface deformation caused by the radial agreement between the fitting segment and the high-rigidity partition. Thus, the outward surface deformation can be minimized by the arrangement in which none of the fitting segments corresponds to the low-rigidity partition.
- A fourth characteristic feature of the present invention lies in that at least one of the plurality of fitting segments is configured to radially overlap the partition that is provided with at least one of the contact portion and the lock mechanism in the radial direction.
- With the above-noted arrangement, the fitting segment agrees with the high-rigidity partition if it is unavoidable that any of the fitting segments radially agrees with any of the partitions. As a result, the outward surface deformation can be minimized even if somewhat deformation inevitably occurs, thereby to suppress overall deformation of the driven rotary element as much as possible.
- A fifth characteristic feature of the present invention lies in that the connecting element has an axial support portion that supports in a through bore formed in the driving rotary element.
- With the above-noted arrangement, the connecting element is allowed to have a function to axially support the driving rotary element. Thus, the connecting element axially supports the driving rotary element to reliably maintain the driving rotary element coaxially with the driven rotary element, while the construction can be simplified. As a result, the posture of the driven rotary element is stabilized.
- A sixth characteristic feature of the present invention lies in providing a guide mechanism for guiding and positioning the driven rotary element and the connecting element in the predetermined rotational phase.
- With the above-noted arrangement, the driven rotary element and the connecting element can be guided and positioned in the predetermined rotational phase through the guide mechanism, which facilitates the positioning of the driven rotary element and the connecting element.
-
-
Fig. 1 is an overall view of a valve timing control device according to a first embodiment of the present invention; -
Fig. 2 is a cross-sectional view of the valve timing control device as viewed along arrows II-II ofFig. 1 ; -
Fig. 3 is a cross-sectional view of a principal portion of the valve timing control device according to the first embodiment of the present invention; -
Fig. 4 is a cross-sectional view of the valve timing control device as viewed along arrows IV-IV ofFig. 3 ; -
Fig. 5 is an exploded perspective view of the valve timing control device according to the first embodiment of the present invention; -
Fig. 6 is a cross-sectional view of the valve timing control device according to a second embodiment of the present invention; -
Fig. 7 is a perspective view of a connecting element according to a modified embodiment; and -
Fig. 8 is a perspective view of a connecting element according to another modified embodiment. - A valve timing control device according to an embodiment of the present invention that is applied to an automobile engine will be described hereinafter in reference to
Figs. 1 and5 . - Referring to
Fig. 1 , the valve timing control device is provided with a steel housing 1 (an example of a driving rotary element) that is synchronously rotatable with a crankshaft C of an engine, and an aluminum inner rotor 3 (an example of a driven rotary element) that is synchronously rotatable with acamshaft 2 of the engine. Thehousing 1 and theinner rotor 3 are coaxially arranged on an axis X. - Referring to
Figs. 1 to 4 , thehousing 1 includes afront plate 4 mounted on a front side thereof opposite to thecamshaft 2, asprocket 5 mounted on a rear side thereof adjacent to thecamshaft 2, and anouter rotor 6 mounted between thefront plate 4 and thesprocket 5. Thefront plate 4,sprocket 5 andouter rotor 6 are fixedly screwed. Here, thehousing 1 may be integrally formed as a unit instead of fixedly screwing thefront plate 4,sprocket 5 andouter rotor 6 together. A rear plate may be mounted instead of thesprocket 5, and the sprocket may be provided at an outer circumference of theouter rotor 6. - When the crankshaft C is rotated, a rotational driving force is transmitted to the
sprocket 5 through a power transmission mechanism (not shown) to rotate theouter rotor 6 in a rotational direction S (seeFig. 2 ). As theouter rotor 6 is rotated, theinner rotor 3 is rotated in the rotational direction S to rotate thecamshaft 2. Then, a cam (not shown) provided in thecamshaft 2 pushes down on an intake valve (not shown) of the engine. - As shown in
Figs. 2 and4 , a plurality offirst partitions 8 project inward in a radial direction from an inner circumference of theouter rotor 6. Thefirst partitions 8 are spaced apart from each other along the rotational direction S. A plurality ofsecond partitions 9 project outward in the radial direction from an outer circumference of theinner rotor 3. Thesecond partitions 9 are also spaced apart from each other along the rotational direction S in the same manner as thefirst partitions 8. Thefirst partitions 8 are configured to divide space between theouter rotor 6 and theinner rotor 3 into a plurality of fluid pressure chambers. Thesecond partitions 9 are configured to divide each of the fluid pressure chambers into anadvanced angle chamber 11 and aretarded angle chamber 12. In order to prevent leakage of engine oil between theadvanced angle chamber 11 and the regardedangle chamber 12, sealing elements SE are provided in positions of thefirst partitions 8 opposed to the outer circumference of theinner rotor 3 and in positions of thesecond partitions 9 opposed to the inner circumference of theouter rotor 6, respectively. - Referring to
Figs. 1 and2 , within theinner rotor 3, a connectingelement 22 and thecamshaft 2 are formed anadvanced angle passage 13 for connecting eachadvanced angle chamber 11 to a feed/discharge mechanism KK for allowing and intercepting feed or discharge of engine oil, aretarded angle passage 14 for connecting each regardedangle chamber 12 to the feed/discharge mechanism KK, and alock passage 15 for connecting the feed/discharge mechanism KK to a lock mechanism RK for locking theinner rotor 3 andouter rotor 6 in a predetermined relative rotational phase. - The feed/discharge mechanism KK includes an oil pan, an oil motor, a fluid control valve OCV for allowing and intercepting feed or discharge of engine oil to/from the
advanced angle passage 13 and theretarded angle passage 14, a fluid switch valve OSV for allowing and intercepting feed or discharge of engine oil to/from thelock passage 15, and an electric control unit ECU for controlling operation of the fluid control valve OCV and fluid switch valve OSV. As the feed/discharge mechanism KK is controlled, the relative rotational phase of theinner rotor 3 andouter rotor 6 is displaced in an advanced angle direction (arrow S1 inFig. 2 ) or a regarded angle direction (arrow S2 inFig. 2 ) or is maintained in a desired phase. - Referring to
Figs. 1 to 5 , theinner rotor 3, connectingelement 22 andcamshaft 2 are fastened through abolt 21. Thebolt 21 is fastened to afemale screw 2b formed in the back of a receivingbore 2c formed in an extreme end of thecamshaft 2. With such an arrangement, theinner rotor 3 is integrally assembled to the extreme end of thecamshaft 2 through the connectingelement 22. - More particularly, a first hollow 23 for accommodating the head of the
bolt 21 is formed in a front surface of theinner rotor 3, while a second hollow 24 (an example of a recess) is formed in a rear surface of theinner rotor 3 for receiving press-fittingly a front part 26 (an example of a press-fitting portion) of the connectingelement 22. A throughbore 25 is formed between the first hollow 23 and the second hollow 24 for receiving thebolt 21. - As illustrated in
Fig. 5 , a plurality ofcutaway segments 27 are spaced apart from each other along the rotational direction S in thefront part 26 of the connectingelement 22. Each section defined between theadjacent cutaway segments 27 acts as afitting segment 28 that is press-fitted into an inner circumference of the second hollow 24. A plurality of thefitting segments 28 are arranged along a circumferential direction of the connectingelement 22 at intervals of 90 degrees, for example. A width of eachfitting segment 28 in an axial direction is substantially the same as or greater than a depth of the second hollow 24. A rear part 29 (an example of an axial support portion) of the connectingelement 22 is supported in a round bore 30 of thesprocket 5. This enables the connectingelement 22 to have a function to axially support thehousing 1. Thus, theinner rotor 3 and thehousing 1 are securely maintained in a coaxial relationship while the construction can be simplified, which stabilizes the posture of theinner rotor 3. - The connecting
element 22 has anopening 31 formed in a front surface thereof for receiving thebolt 21, and arecess 32 formed in a rear surface thereof for receiving the extreme end of thecamshaft 2. A front pin-receivinghole 3a is formed in theinner rotor 3, a rear pin-receivinghole 2a is formed in the extreme end of thecamshaft 2, and an intermediate pin-receivinghole 22a is formed in the connectingelement 22, respectively. A gap between the throughbore 25 of theinner rotor 3 and thebolt 21, a gap between the opening 31 of the connectingelement 22 and thebolt 21, and a gap between the receiving bore 2c of thecamshaft 2 and thebolt 21 act together as theadvanced angle passage 13. - As illustrated in
Fig. 3 , a pin P is inserted into the pin-receivinghole 3a of theinner rotor 3 and the pin-receivinghole 22a of the connectingelement 22 to press fit thefront part 26 of the connectingelement 22 to the second hollow 24 of theinner rotor 3. Then, the pin P advances into the pin-receivinghole 2a formed in the extreme end of thecamshaft 2 to insert the extreme end of thecamshaft 2 to therecess 32 of the connectingelement 22. As a result, theinner rotor 3, the connectingelement 22 and the extreme end of thecamshaft 2 are positioned in the predetermined relative rotational phase, thereby to form theadvanced angle passage 13, theretarded angle passage 14 and thelock passage 15. - More particularly, the pin P and pin-receiving
holes inner rotor 3 and the connectingelement 22 to be positioned in the predetermined relative rotational phase. Theinner rotor 3 and the connectingelement 22 are guided and positioned in the predetermined rotational phase through the guide mechanism (pin P and pin-receivingholes inner rotor 3 and the connectingelement 22. - As shown in the arrangement shown in
Fig. 4 , none of thefitting segments 28 may overlap any of thesecond partitions 9, for example. When the connectingelement 22 is press-fitted into the second hollow 24, the portions of theinner rotor 3 corresponding to the fitting segments are somewhat deformed to be radially enlarged, but are not associated with any of thesecond partitions 9. Thus, none of thesecond partitions 9 are deformed in corners. As a result, the outward surface deformation of the wholeinner rotor 3 can be minimized. In addition, fittedsegments 41 in theinner rotor 3 are all deformed to the same extent, which can prevent eccentricity of theinner rotor 3. - While
Fig. 4 shows the configuration in which none of thefitting segments 28 overlap thesecond partitions 9, it is sufficient that at least one of thefitting segments 28 does not overlap the correspondingsecond partition 9. This is because the deformation of theinner rotor 3 can be a minimum since the portion where thefitting segment 28 does not overlap the correspondingsecond partition 9 has no influence on the change of the posture of thesecond partition 9. - In the present invention, it is not that all of the
fitting segments 28 should never radially overlap the correspondingsecond partitions 9. More particularly, thesecond partitions 9 may be arranged so as not to overlap centerlines CL of the respectivefitting segments 28 extending in the radial direction. In such an arrangement, the deformation of theinner rotor 3 caused by the pressing of thefitting segments 28 becomes a maximum on the centerlines CL of thefitting segments 28 extending in the radial direction. Thus, the outward surface deformation of the wholeinner rotor 3 can be minimized by arranging thesecond partitions 9 so as not to overlap the centerlines of thefitting segments 28. In the construction of the present invention in which the centerlines CL of all thefitting segments 28 extending in the radial direction are arranged so as not to overlap the correspondingsecond partitions 9 in the radial direction, any of thesecond partitions 9 is not influenced by or is influenced a little by the deformation of theinner rotor 3 caused by the pressing of thefitting segments 28. - Referring to
Fig. 6 , part of thefitting segments 28 overlaps thesecond partition 9 that is provided with the lock mechanism RK of the plurality ofsecond partitions 9 in the radial direction, and the remainingfitting segments 28 do not overlap thesecond partitions 9 that are not provided with the lock mechanism RK. Thesecond partition 9 that is provided with the lock mechanism RK is greater than the remaining second partitions in circumferential dimension and rigidity because the lock pin should be provided. Thus, the second partition that is provided with the lock mechanism RK is referred to as a high-rigidity partition 9a, while the remaining second partitions are referred to as low-rigidity partitions 9b hereinafter. - In the embodiment shown in
Fig. 6 , while threefitting segments 28 can be arranged so as not to overlap any of thesecond partitions 9, one fittingsegment 28 inevitably overlaps any one of thesecond partitions 9. In such a case, the high-rigidity partition 9a is selected as thesecond partition 9 to overlap. More particularly, the high-rigidity partition 9a is not much subject to the influence of the pressing of the connectingelement 22 because of its high rigidity. Therefore, the outward surface deformation in the corresponding fittedsegment 41 is diminished, which results in the minimal overall deformation of theinner rotor 3. The fittedsegments 41 fitted to the remaining threefitting segments 28 are formed in cylindrical portions of theinner rotor 3. Thus, while the cylindrical portions are deformed by the pressing of thefitting segments 28, such deformation has no influence on any of the low-rigidity partitions 9b. - In the second embodiment, only one
fitting segment 28 radially overlaps the high-rigidity partition 9a that is provided with the lock mechanism RK. Instead, a plurality of thefitting segments 28 may overlap one high-rigidity partition 9a. Alternatively, a plurality of the high-rigidity partitions 9a may correspond to the plurality offitting segments 28, respectively. In any case, the above-described effect of suppressing the deformation of theinner rotor 3 can be achieved. - Each
fitting segment 28 of the connectingelement 22 may be shaped as shown inFigs. 7 and 8 . More particularly, thefitting segment 28 may be formed in a region extending from the front side to the back side of the connectingelement 22 as shown inFig. 7 . - Alternatively, as shown in
Fig. 8 , the connectingelement 22 may have a combination ofcutaway parts 27 each having a flat surface andfitting segments 28 each having a cylindrical surface. Thefitting segments 28 may be formed by chamfering four corners of a square material. Alternatively, thecutaway parts 27 may be formed by cutting four sections away from a disk material to flat surfaces. - Any of the above-described arrangements can provide the connecting
element 22 that can minimize the deformation of theinner rotor 3. The connectingelement 22 shown inFig. 8 , in particular, is easy to process in shape, and thus can be manufactured cost-effectively. - The present invention is applicable to a valve timing control device for an internal combustion engine of an automobile, for example.
Claims (6)
- A valve timing control device comprising:a driving rotary element (1) synchronously rotatable with a crankshaft (C);a driven rotary element (3) mounted coaxially with the driving rotary element (1) and synchronously rotatable with a camshaft (2);a plurality of second partitions (9) provided in the driven rotary element (3) each for dividing a fluid pressure chamber formed between the driving rotary element (1) and the driven rotary element (3) into a retarded angle chamber (12) and an advanced angle chamber (11); anda connecting element (22) having a press fitting portion (26) that is press-fitted into a recess (24) formed in the driven rotary element (3) for connecting the driven rotary element (3) to the camshaft (2), and whereinthe press fitting portion (26) is provided by a plurality of fitting segments (28) such that exclusively the fitting segments (28) are in press fitting contact with an inner circumference of the recess (24), whereinat least one of centerlines (CL) of the fitting segments (28) extending in a radial direction does not overlap any of the second partitions (9), characterized in that the fitting segments (28) are spaced apart from each other along a rotational direction by a plurality of cutaway segments (27), and in that the recess (24) has a cylindrical shape.
- The valve timing control device as defined in claim 1, wherein all of the radially extending centerlines (CL) of the fitting segments (28) are configured not to overlap any of the second partitions (9).
- The valve timing control device as defined in claim 1, wherein all of the radially extending centerlines (CL) of the fitting segments (28) are configured not to radially overlap any of the second partitions (9) other than the second partition (9) that is provided with at least one of a contact portion coming into contact with the driving rotary element (1) for limiting relative movement between the driving rotary element (1) and the driven rotary element (3) and a lock mechanism (RK) for locking the driving rotary element (1) and the driven rotary element (3) in a predetermined rotational phase.
- The valve timing control device as defined in claim 3, wherein at least one of centerlines (CL) of the plurality of fitting segments (28) is configured to radially overlap the second partition (9) that is provided with at least one of the contact portion and the lock mechanism (RK) in the radial direction.
- The valve timing control device as defined in any of claims 1 to 4, wherein the connecting element (22) has an axial support portion (29) that is supported in a through bore (30) formed in the driving rotary element (1).
- The valve timing control device as defined in any of claims 1 to 5, further comprising a guide mechanism (P, 3a, 22a) for guiding and positioning the driven rotary element (3) and the connecting element (22) in the predetermined rotational phase.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2011033813A JP5321925B2 (en) | 2011-02-18 | 2011-02-18 | Valve timing control device |
PCT/JP2012/051356 WO2012111388A1 (en) | 2011-02-18 | 2012-01-23 | Valve opening/closing timing control device |
Publications (3)
Publication Number | Publication Date |
---|---|
EP2677126A1 EP2677126A1 (en) | 2013-12-25 |
EP2677126A4 EP2677126A4 (en) | 2014-03-26 |
EP2677126B1 true EP2677126B1 (en) | 2016-08-03 |
Family
ID=46672327
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP12747141.5A Not-in-force EP2677126B1 (en) | 2011-02-18 | 2012-01-23 | Valve opening/closing timing control device |
Country Status (6)
Country | Link |
---|---|
US (1) | US8910604B2 (en) |
EP (1) | EP2677126B1 (en) |
JP (1) | JP5321925B2 (en) |
KR (1) | KR101475671B1 (en) |
CN (1) | CN103339348B (en) |
WO (1) | WO2012111388A1 (en) |
Families Citing this family (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102012208496B4 (en) * | 2012-05-22 | 2013-12-05 | Schaeffler Technologies AG & Co. KG | Camshaft adjustment device |
JP5991091B2 (en) | 2012-09-04 | 2016-09-14 | アイシン精機株式会社 | Valve timing control device |
DE102013107431A1 (en) * | 2013-07-05 | 2015-01-08 | Hilite Germany Gmbh | Rotor for a camshaft adjuster with improved properties |
JP2015045282A (en) * | 2013-08-28 | 2015-03-12 | アイシン精機株式会社 | Valve opening/closing timing control device |
JP6273801B2 (en) | 2013-11-29 | 2018-02-07 | アイシン精機株式会社 | Valve timing control device |
JP6187203B2 (en) * | 2013-11-29 | 2017-08-30 | アイシン精機株式会社 | Valve timing control device |
DE102013226454B4 (en) * | 2013-12-18 | 2020-11-26 | Schaeffler Technologies AG & Co. KG | Connection principle of a multi-part rotor for a hydraulic camshaft adjuster |
DE102013226466A1 (en) * | 2013-12-18 | 2015-06-18 | Schaeffler Technologies AG & Co. KG | Construction principle of a split rotor for a hydraulic camshaft adjuster |
DE102013226445B4 (en) * | 2013-12-18 | 2020-11-26 | Schaeffler Technologies AG & Co. KG | Camshaft centering in the split rotor of a hydraulic camshaft adjuster and the associated manufacturing process |
JP6217438B2 (en) * | 2014-02-14 | 2017-10-25 | アイシン精機株式会社 | Valve timing control device |
DE102015113356A1 (en) * | 2015-08-13 | 2017-02-16 | Thyssenkrupp Ag | Adjustable camshaft with a phase plate |
JP2017115600A (en) * | 2015-12-21 | 2017-06-29 | アイシン精機株式会社 | Valve opening timing control device |
DE102017113361B3 (en) * | 2017-06-19 | 2018-09-27 | Schaeffler Technologies AG & Co. KG | Hydraulic camshaft adjuster and method of operating the hydraulic camshaft adjuster |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2010128976A1 (en) * | 2009-05-04 | 2010-11-11 | Gkn Sinter Metals, Llc | Adhesive joining for powder metal components |
Family Cites Families (19)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2001029377A1 (en) * | 1999-10-22 | 2001-04-26 | Mitsubishi Denki Kabushiki Kaisha | Valve timing adjusting device |
JP2002180809A (en) * | 2000-10-04 | 2002-06-26 | Denso Corp | Method of manufacturing valve timing adjusting device |
DE10163792A1 (en) * | 2001-12-22 | 2003-07-03 | Ina Schaeffler Kg | Device for alteration of control times of gas change valves in an internal combustion engine, comprises annular disks located between the steel end covers and the light-metal stator |
JP2005155541A (en) * | 2003-11-27 | 2005-06-16 | Mitsubishi Electric Corp | Valve timing adjusting device and its assembling device |
JP4200920B2 (en) * | 2004-02-18 | 2008-12-24 | アイシン精機株式会社 | Valve timing control device |
DE102004019190A1 (en) * | 2004-04-16 | 2005-11-10 | Ina-Schaeffler Kg | Variable phase camshaft drive for IC engine is fitted onto the camshaft by a circular wedge lock axial compactness |
US7475660B2 (en) * | 2004-06-02 | 2009-01-13 | Ina-Schaeffler Kg | Camshaft adjuster |
JP4247624B2 (en) | 2004-12-28 | 2009-04-02 | 株式会社デンソー | Valve timing adjustment device |
JP4161277B2 (en) * | 2005-03-11 | 2008-10-08 | アイシン精機株式会社 | Valve timing control device |
JP4290754B2 (en) * | 2005-08-30 | 2009-07-08 | 三菱電機株式会社 | Valve timing adjustment device |
JP4352338B2 (en) * | 2005-10-25 | 2009-10-28 | アイシン精機株式会社 | Valve timing control device |
JP4626819B2 (en) * | 2006-03-29 | 2011-02-09 | アイシン精機株式会社 | Valve timing control device |
DE102006033977A1 (en) * | 2006-07-22 | 2008-01-24 | Dr.Ing.H.C. F. Porsche Ag | Device and method for adjusting the position of a camshaft adjuster relative to a camshaft |
JP4771168B2 (en) | 2006-12-06 | 2011-09-14 | 株式会社デンソー | Valve timing adjustment device |
JP4851475B2 (en) * | 2008-02-08 | 2012-01-11 | 株式会社デンソー | Valve timing adjustment device |
DE102008011116A1 (en) * | 2008-02-26 | 2009-08-27 | Schaeffler Kg | Camshaft adjuster i.e. blade cell adjuster, for internal-combustion engine of motor vehicle, has set of casings arranged in such manner that three separate axial pressure medium lines are formed |
JP4725655B2 (en) | 2009-02-09 | 2011-07-13 | 株式会社デンソー | Valve timing adjustment device |
JP5440853B2 (en) | 2010-01-08 | 2014-03-12 | アイシン精機株式会社 | Valve timing control device |
DE102010046619A1 (en) * | 2010-09-25 | 2012-03-29 | Bayerische Motoren Werke Aktiengesellschaft | Rotor for a camshaft adjuster and camshaft adjusting system |
-
2011
- 2011-02-18 JP JP2011033813A patent/JP5321925B2/en not_active Expired - Fee Related
-
2012
- 2012-01-23 EP EP12747141.5A patent/EP2677126B1/en not_active Not-in-force
- 2012-01-23 CN CN201280007187.7A patent/CN103339348B/en not_active Expired - Fee Related
- 2012-01-23 KR KR1020137018064A patent/KR101475671B1/en active IP Right Grant
- 2012-01-23 US US13/991,071 patent/US8910604B2/en active Active
- 2012-01-23 WO PCT/JP2012/051356 patent/WO2012111388A1/en active Application Filing
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2010128976A1 (en) * | 2009-05-04 | 2010-11-11 | Gkn Sinter Metals, Llc | Adhesive joining for powder metal components |
Also Published As
Publication number | Publication date |
---|---|
KR20130095312A (en) | 2013-08-27 |
WO2012111388A1 (en) | 2012-08-23 |
CN103339348A (en) | 2013-10-02 |
CN103339348B (en) | 2016-11-23 |
EP2677126A1 (en) | 2013-12-25 |
JP2012172558A (en) | 2012-09-10 |
EP2677126A4 (en) | 2014-03-26 |
US8910604B2 (en) | 2014-12-16 |
US20130247855A1 (en) | 2013-09-26 |
JP5321925B2 (en) | 2013-10-23 |
KR101475671B1 (en) | 2014-12-23 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP2677126B1 (en) | Valve opening/closing timing control device | |
US8910605B2 (en) | Valve timing control device | |
JP2012172558A5 (en) | ||
US8763573B2 (en) | Camshaft adjusting arrangement | |
CN108625922B (en) | Camshaft adjuster for a camshaft arrangement and camshaft arrangement | |
JP7074102B2 (en) | Hydraulic oil control valve and valve timing adjuster | |
JP2012172559A5 (en) | ||
JP6217587B2 (en) | Valve timing control device | |
EP2894304B1 (en) | Valve timing controller | |
US20150059519A1 (en) | Camshaft adjuster and separating sleeve for a camshaft adjuster | |
WO2016068178A1 (en) | Valve-opening-closing-timing control device | |
EP3321479B1 (en) | Valve opening/closing timing control apparatus | |
EP2761144B1 (en) | Valve timing controller | |
US10174646B2 (en) | Valve opening and closing timing control apparatus | |
CN110730857B (en) | Camshaft adjuster having a stator and a rotor with a concentric spring receptacle | |
US20200141289A1 (en) | Valve timing controller | |
US20170101904A1 (en) | Camshaft adjuster | |
CN107923274B (en) | Valve timing control device for internal combustion engine | |
CN112513431A (en) | Insert for camshaft phaser and camshaft phaser |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
17P | Request for examination filed |
Effective date: 20130916 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R079 Ref document number: 602012021226 Country of ref document: DE Free format text: PREVIOUS MAIN CLASS: F01L0001356000 Ipc: F01L0001344000 |
|
A4 | Supplementary search report drawn up and despatched |
Effective date: 20140224 |
|
RIC1 | Information provided on ipc code assigned before grant |
Ipc: F01L 1/047 20060101ALI20140218BHEP Ipc: F01L 1/344 20060101AFI20140218BHEP |
|
DAX | Request for extension of the european patent (deleted) | ||
17Q | First examination report despatched |
Effective date: 20140703 |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
INTG | Intention to grant announced |
Effective date: 20160513 |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: EP Ref country code: AT Ref legal event code: REF Ref document number: 817480 Country of ref document: AT Kind code of ref document: T Effective date: 20160815 |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: FG4D |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R096 Ref document number: 602012021226 Country of ref document: DE |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 6 |
|
REG | Reference to a national code |
Ref country code: NL Ref legal event code: MP Effective date: 20160803 |
|
REG | Reference to a national code |
Ref country code: LT Ref legal event code: MG4D |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: MK05 Ref document number: 817480 Country of ref document: AT Kind code of ref document: T Effective date: 20160803 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: NL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160803 Ref country code: IS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161203 Ref country code: NO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161103 Ref country code: IT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160803 Ref country code: RS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160803 Ref country code: LT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160803 Ref country code: HR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160803 Ref country code: FI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160803 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LV Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160803 Ref country code: AT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160803 Ref country code: PT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161205 Ref country code: ES Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160803 Ref country code: GR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161104 Ref country code: SE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160803 Ref country code: PL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160803 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: RO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160803 Ref country code: EE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160803 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R097 Ref document number: 602012021226 Country of ref document: DE |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SM Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160803 Ref country code: BG Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20161103 Ref country code: SK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160803 Ref country code: BE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160803 Ref country code: CZ Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160803 Ref country code: DK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160803 |
|
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
26N | No opposition filed |
Effective date: 20170504 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160803 |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: PL |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20170123 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MC Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160803 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170131 Ref country code: LI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170131 |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: MM4A |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170123 Ref country code: LU Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170123 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 7 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170123 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20170123 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: AL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160803 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: HU Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO Effective date: 20120123 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: CY Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20160803 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160803 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: TR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20160803 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20201210 Year of fee payment: 10 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20210112 Year of fee payment: 10 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R119 Ref document number: 602012021226 Country of ref document: DE |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20220802 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20220131 |